US5090226A - Motor driven flaring device - Google Patents

Motor driven flaring device Download PDF

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Publication number
US5090226A
US5090226A US07/665,461 US66546191A US5090226A US 5090226 A US5090226 A US 5090226A US 66546191 A US66546191 A US 66546191A US 5090226 A US5090226 A US 5090226A
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US
United States
Prior art keywords
rotational drive
drive shaft
motor driven
flaring device
pipe
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US07/665,461
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English (en)
Inventor
Katsushi Takeoka
Tsuyoshi Ohashi
Yoshiharu Ikenaka
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Inoac Corp
Rex Industries Co Ltd
Original Assignee
Inoac Corp
Rex Industries Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Inoac Corp, Rex Industries Co Ltd filed Critical Inoac Corp
Assigned to INOAC CORPORATION, REX INDUSTRIES CO., LTD. reassignment INOAC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: IKENAKA, YOSHIHARU, OHASHI, TSUYOSHI, TAKEOKA, KATSUSHI
Application granted granted Critical
Publication of US5090226A publication Critical patent/US5090226A/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23K—SOLDERING OR UNSOLDERING; WELDING; CLADDING OR PLATING BY SOLDERING OR WELDING; CUTTING BY APPLYING HEAT LOCALLY, e.g. FLAME CUTTING; WORKING BY LASER BEAM
    • B23K9/00—Arc welding or cutting
    • B23K9/32—Accessories
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D41/00—Application of procedures in order to alter the diameter of tube ends
    • B21D41/02—Enlarging
    • B21D41/021—Enlarging by means of tube-flaring hand tools
    • B21D41/023—Enlarging by means of tube-flaring hand tools comprising rolling elements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D41/00—Application of procedures in order to alter the diameter of tube ends
    • B21D41/02—Enlarging
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T408/00—Cutting by use of rotating axially moving tool
    • Y10T408/65—Means to drive tool
    • Y10T408/675—Means to drive tool including means to move Tool along tool-axis
    • Y10T408/6771—Means to drive tool including means to move Tool along tool-axis with clutch means

Definitions

  • the present invention relates to a flaring tool for gradually spreading a front end of a pipe into a conical shape, and more particularly, it relates to a motor driven flaring device.
  • a simple manual flaring tool having a tool body 1 which has a rotatable shaft 7 with handle 3 at its upper end, as shown in FIG. 12.
  • the rotatable shaft 7 is rotatably screwed in the upper end of the tool body 1.
  • the rotatable shaft 7 is provided on its lower end with an eccentric cone 5, as shown in FIGS. 13 and 14.
  • the eccentric cone 5 is pressed against the end of the pipe P and then the handle 3 is manually rotated by an operator to rotate the eccentric cone 5 while pressing the eccentric cone 5 down onto the pipe end to thereby spread the latter into a conical shape.
  • the pipe end is flared from the inner diameter side thereof into a conical shape corresponding to the eccentric cone 5.
  • a rotation axis Y of the eccentric cone 5 about which it rotates is inclined or eccentric with respect to the axis X of the rotatable shaft 7.
  • the center of rotation of the eccentric cone 5 at the front end thereof (apex of the cone) is fixed and is always located on the axis of the rotatable shaft 7, so that the pipe end can be gradually and smoothly flared.
  • numeral 9 designates a holder plate which holds the pipe P and has an array of holes 6 in which the pipe P to be held is inserted.
  • the holes 6 are chambered or tapered at the entrance ends thereof into a conical shape corresponding to the conical peripheral surface of the eccentric cone 5.
  • the holder plate 9 is split into two plate elements 9a and 9b (FIG. 12), each having semi-circular recesses defining the holes 6 when combined.
  • the pipe P is first fitted in the associated hole 6 and is then firmly held therein by the holder plate 9 when a threaded handle 8 attached to the tool body 1 is fastened.
  • the primary object of the present invention is to provide a simple motor driven flaring device which can eliminate the above-mentioned drawbacks of the prior art.
  • a motor driven flaring device in which a rotatable eccentric cone an apex of which defines a fixed center of rotation is pressed, while rotating, against an end of a pipe to be flared to spread the end of the pipe into a conical shape, comprising, a body having a motor incorporated therein and having an output shaft to be connected to a drive source, said body being provided with a female threaded portion, a rotational drive shaft which is connected to the output shaft of the motor so as to relatively move in the axial direction thereof, said eccentric cone being rigidly secured to the rotational drive shaft, a feed screw shaft member which is connected to the rotational drive shaft and is screw-engaged by the female threaded portion of the body so as to rotate and move in the axial direction thereof, a one-direction rotation transmission means between the rotational drive shaft and the feed screw shaft member for transmitting the rotation of the rotational drive shaft to the feed screw shaft member only in one direction, and an elastic means between the
  • the motor is located below the rotational drive shaft so that the output shaft of the motor is substantially in parallel with the rotational drive shaft.
  • a clutch member is provided between the rotational drive shaft and the feed screw shaft member to selectively disengage the connection therebetween through the one-direction rotation transmission means in accordance with the axial movement of the feed screw shaft member.
  • a positioning plate is provided, which is rotatably mounted to one of the split plates to restrict the axial position of a pipe to be flared in the pipe holder.
  • the eccentric cone itself is similar to that of the prior art shown in FIGS. 13 and 14.
  • the axis of the rotation of the eccentric cone is inclined with respect to the axis of the rotational drive shaft, but the apex of the cone which defines a fixed center of rotation is immovably located on the axis of the rotational drive shaft.
  • the eccentric cone is rotated by the motor at a predetermined number of revolutions reduced by the reduction gear device.
  • the rotational drive shaft rotates, the rotation thereof is transmitted to the feed screw shaft, so that the later moves in the axial direction through a feed screw mechanism which is constituted by the female and male threads formed on the body and the feed screw shaft, respectively.
  • the axial movement of the feed screw shaft is transmitted to the rotational drive shaft, and accordingly, to the eccentric cone through the elastic means, so that the eccentric cone is moved in the same axial direction.
  • the eccentric cone is strongly pressed against the end of the pipe to be flared while rotating to spread the pipe end into a conical shape.
  • the eccentric cone Upon completion of the flaring, the eccentric cone is no longer able to move in the axial direction, so that it idles in the pipe end. Accordingly, a further rotation of the motor causes the feed screw shaft to move further in the axial direction while compressing the biasing means, so that the connection of the rotational drive shaft and the feed screwshaft is broken, thus resulting in a null operation of the one-direction rotation transmission means.
  • the idle rotation of the eccentric cone after the completion of the flaring prevents the tool, i.e., the eccentric cone from being damaged or broken due to the overload and also contributes to production of a uniform and precisely flared end of the pipe.
  • the flaring device can be made compact and handy.
  • the engagement and disengagement of the one-direction rotation transmission means are effected by the clutch member.
  • the pipe to be flared can be easily attached to the flaring device using the pipe holder.
  • the pipe can be easily and definitely positioned at a predetermined position of the pipe holder by inserting the pipe in the pipe holder until the pipe end comes into surface contact with the side face of the positioning plate, so that no positioning of the pipe depends on the operator's intuition.
  • FIG. 1 is a longitudinal sectional view of a motor driven flaring device according to the present invention
  • FIG. 2 is a front elevational view of an appearance of a motor driven flaring device, shown in FIG. 1;
  • FIG. 3 is a right side elevational view of a motor driven flaring, device shown in FIG. 2:
  • FIG. 4A is a longitudinal sectional view of a main part of a motor driven flaring device shown in FIG. 1, shown at a start position;
  • FIG. 4B is a sectional view taken along the line 4B and 4B in FIG. 4A;
  • FIG. 5A is a view similar to FIG. 4A, but shown at a position of completion of the flaring;
  • FIG. 5B is a sectional view taken along the line 5B and 5B in FIG. 5A;
  • FIG. 6A is a view similar to FIG. 4A, but shown at an idling position after the completion of the flaring;
  • FIG. 6B is a sectional view taken along the line 6B and 6B in FIG. 6A;
  • FIG. 7A is a view similar to FIG. 4A, but shown at an idling position upon reversing;
  • FIG. 7B is a sectional view taken along the line 7B and 7B in FIG. 7A;
  • FIG. 8A to 8C are sectional views taken along the lines 8A--8A, 8B--8B and 8C--8C in FIG. 1, respectively;
  • FIGS. 9A and 9B are right side elevational views of a holder shown in FIG. 1, shown at open and closed positions of a positioning plate thereof, respectively;
  • FIG. 10 is an enlarged view of a positioning plate shown in FIGS. 9A and 9B;
  • FIG. 11 is a partial perspective view of a nut member shown in FIG. 1;
  • FIG. 12 is a perspective view of a known manual flaring tool
  • FIGS. 13 and 14 are explanatory vies of an eccentric cone shown at different rotation phases thereof, for explaining how to flare a pipe end;
  • FIG. 15 is a schematic view of a pipe before and after flaring.
  • FIGS. 1, 2, and 3 show an embodiment of a motor driven flaring device according to the present invention.
  • the flaring device has a pistol-shaped body 11 having a grip portion 13 which is provided on its lower portion with a battery receptacle 14 in which a battery B is received.
  • the battery B is connected to a motor M incorporated in the body 11 by means of a cord 15 through a drive switch 17.
  • the motor M is rotated in the left (L) and the right hand (R) directions, respectively, as shown in FIG. 3.
  • the drive switch 17 is automatically made OFF when the operational force is released therefrom.
  • the battery B can be removed from the battery receptacle 14 for exchange by opening a bottom cover 19 provided at the lower end of the body 11.
  • the motor M is disposed above the upper end of the grip portion 13 in the body 11.
  • the motor M has an output shaft 21 which is connected to a rotational drive shaft 27 through a reduction gear device 23 which is composed of a gear train including a certain number of gears W1, W2, W3, etc., which are rotatably supported by respective bearings.
  • the rotational drive shaft 27 has an annular boss 31 which is connected to a gear shaft 25 of the terminal end gear W3 of the reduction gear device 23 through a spline 29, so that the rotation of the motor M is reduced and transmitted to the rotational output shaft 27.
  • the annular boss 31 is made integral with the rotational drive shaft 27 by a knock-pin 33.
  • the annular boss 31 is provided on its outer peripheral surface with an axial groove 35 which extends in the axial direction, so that a ratchet lever 39 which constitutes a one-direction rotation transmission mechanism is rotatably or swingably supported in the axial groove 35 through a pivot pin 37.
  • the ratchet lever 39 is continuously biased upward at the rear end thereof by a biasing spring 41 which is provided between the boss 31 and the rear end (left end in FIG. 1) of the ratchet lever 39, in FIG. 1. Consequently, the ratchet lever 39 is always biased to rotate in the clockwise direction about the pivot pin 37 by the spring 41 in FIG. 1.
  • the ratchet lever 39 is provided on its front end (right end in FIG. 1) with a ratchet pawl 43 which will be discussed hereinafter.
  • the motor M is displaced below the rotational output shaft 27 so that the drive shaft 21 of the motor M is substantially in parallel with the axis of the rotational output shaft 27. This makes it possible to realize a compact and handy pistol-shaped flaring device.
  • the rotational output shaft 27 is provided on its front end with an eccentric cone 47 which juts out from the body 11.
  • the eccentric cone 47 per se is the same as that of FIGS. 12 and 13, so that it has a rotation axis Y inclined or eccentric with respect to the axis X of the rotational output shaft 27. Consequently, the rotation axis Y describes a conical generatrix when the eccentric cone 47 rotates. Note that the front end (apex of) of the eccentric cone remains at a constant position (fixed position) on the axis X of the rotational output shaft 27 during the rotation of the eccentric cone 47.
  • an annular feed screw shaft 49 which is rotatable and movable in the axial direction relative to the rotational output shaft 27.
  • the feed screw shaft 49 is provided on its outer periphery with a threaded portion (male thread) 49a which is screw-engaged by a threaded hole (female thread) 51 of a nut member 53 integral with the body 11.
  • the feed screw shaft (movable element) 49 and the nut member (immovable element) 53 constitute a feed screw mechanism in which when the feed screw shaft 49 rotates, it moves in the axial direction relative to the immovable nut member 53.
  • the rotational output shaft 27 is provided at its front end with a larger diameter portion 28. Between the larger diameter portion 28 and the feed screw shaft 49 is provided a first spring 55 which continuously biases the eccentric cone 47 in the right hand direction in FIG. 1. On the other hand, a second spring 59 which is weaker than the first spring 55 is provided in the rear end of the feed screw shaft 49 and between the rear end of the feed screw shaft 49 and the boss 31 to bias both in a direction away from one another.
  • the feed screw shaft 49 is provided at its rear end with a flanged projection 61 which is in turn provided, on its outer periphery, with an axially extending ratchet groove 62 (FIG. 4B) in which the ratchet pawl 32 can be engaged. Consequently, the engaging position of the ratchet pawl 43 with the axial ratchet groove 62 varies in accordance with the axial displacement of the feed screw shaft 49.
  • the ratchet pawl 43 has a cross-sectional shape which changes in the axial direction thereof, as shown in FIGS. 8A, 8B and 8c. Namely, as viewed from the front (the side adjacent to the eccentric cone 47), the ratchet pawl 43 has a first tapered bottom surface 43a to gradually decrease the width thereof toward the right (FIG. 8A), a generally V-shaped bottom surface 43b (FIG. 8B) and a second tapered bottom surface 43c to gradually decrease the width of the ratchet pawl 43 toward the left (FIG. 8C), in this order.
  • the inclination angle of the first tapered bottom surface 43a, the V-shaped bottom surface 43b and the second tapered bottom surface 43c is for example around 18°.
  • a pipe holder 71 which is adapted to attach the flaring device to a pipe P to be flared.
  • the pipe holder 71 is shown in detail in FIGS. 9A, 9B, and 10.
  • the pipe holder 71 has a holder body 73, and a holder ring 75 (FIG. 1) which connects the holder body 73 to the nut member 53 of the tool body 11.
  • the holder ring 75 is provided on its front and rear end faces with a plurality of inwardly flanged projections 77 (rear side) and 79 (front side). In the illustrated embodiment, there are three inner radial projections 77 (79) provided on each end face of the holder ring 75 and spaced from one another at a predetermined angular distance.
  • the rear projections 77 are fitted in corresponding grooves 91 (FIG. 11) which are formed in the nut member 53.
  • Each of the grooves 91 has a circumferential groove portion 91a which circumferentially extends from the entrance of the groove 91 and which is gradually inclined toward the rear end of the nut member 53 at a slight inclination angle ⁇ , as shown in FIG. 11.
  • Behind the front radial projections 79 are located associated radial projections 80 of the holder body 73, so that the front end faces of the radial projections 80 come into surface contact with the rear end faces of the associated radial projections 79.
  • the holder body 73 Upon assembly, the holder body 73 is opposed to the holder ring 75 in such a way that there is a difference in phase between the projections 80 of the holder body 73 and the projections 79 of the holder ring 75, so that the projections 80 are disposed between the projections 79 as viewed from the axial direction. Then, the projections 80 of the holder body 73 are axially moved in the holder ring 75, and thereafter, the holder body 73 and the holder ring 75 are relatively rotated through an appropriate angular displacement to bring the projections 80 behind the associated projections 79, whereby the holder body 73 and the holder ring 75 are integrally interconnected.
  • the rear projections 77 of the holder ring 75 are first fitted in the associated grooves 91 of the nut member 53 and are then rotated, so that the projections 77 are moved in and along the circumferential inclined groove portions 91a of the associated grooves 90. Due to the inclination of the groove portions 91a, the holder ring 75 is moved in the axial direction toward the nut member 53, and accordingly, the holder body 73 is strongly urged toward the nut member 53, thus resulting in a firm connection of the nut member 53 and the pipe holder 71.
  • the holder body 73 has a pair of split type plates 95a and 95b which can be opened and closed, as shown in FIGS. 9A and 9B.
  • the plates 95a and 95b are connected to each other at their one end through a pivot pin 93 so as to relatively rotate, and at their opposite ends by a fastening bolt 94 having a knurled handle 98 for opening and closing.
  • the base end of the fastening bolt 94 is rotatably connected to the plate 95b through a pivot pin 99, so that when the fastening bolt 94 is rotated in the counterclockwise direction in FIG. 9A, as shown by a phantom line 94', the other plate 95a is free from the fastening bolt 94.
  • the plates 95a and 95b can be opened to clamp the pipe P in the holder body 73 of the pipe holder 71.
  • the fastening bolt 94 which is returned to a position shown at a solid line in FIG. 9A is fastened by rotating the handle 98 thereof to firmly and immovably hold the pipe P in the pipe holder 71.
  • the plates 95a and 95b have semi-circular openings 96a and 96b which define a circular opening 96c having a diameter substantially equal to the outer diameter of the pipe P when the plates 95a and 95b are closed, so that the pipe P can be fitted in the circular opening 96c.
  • the holder body 73 has a positioning plate 81 for positioning the front end of the pipe P, as shown in FIGS. 9A, 9B and 10.
  • the positioning plate 81 restricts the axial position of the pipe P. Namely, the pipe P is inserted in the opening 96c of the pipe holder until the end of the pipe P to be flared comes into contact with the front side face (right side face in FIG. 1) of the positioning plate 81, as shown in FIG. 1.
  • the positioning plate 81 has at its one end a pin hole 92 in which the pivot pin 93 of the plates 95a and 95b is fitted, so that the positioning plate 81 is rotatable or swingable about the pivot pin 93 between an open or inoperative position (FIG. 9B) and a closed or operative position (FIG. 9A).
  • the positioning plate 81 is placed on the holder body 73 on the side thereof adjacent to the nut member 53.
  • the positioning plate 81 is shaped such that it covers the circular opening 96c defined by the semi-circular openings 96a and 96b so as not to exceed the semi-circular area, that is, so as not to cover the center of the circular opening 96c, at the closed position (operative position) shown in FIG. 9A. Consequently, the apex of the eccentric cone 47 can enter the inside of the pipe P which is held in the opening 96c of the holder plates 95a and 95b without being interrupted by the positioning plate 81, as shown in FIG. 1.
  • the eccentric cone 47 moves forward while eccentrically rotating, upon flaring, as mentioned above, the eccentric cone 47 gradually enters the inner diameter of the pipe P while kicking the positioning plate 81 every turn of rotation. Namely, the positioning plate 81 vibrates or rattles during the rotation of the eccentric cone 47. Note that if the positioning plate 81 is large enough to cover the center of the circular opening 96c, the positioning plate 81 interferes with the apex of the eccentric cone 47, so that the latter can not enter the pipe P. It should be appreciated that since the eccentric cone 47 eccentrically rotates, as mentioned above, once the apex thereof passes beyond the positioning plate 81, the eccentric cone 47 can thrust the positioning plate 81 aside while rotating.
  • FIGS. 4A and 4B show the flaring device at a start position.
  • the portion of the ratchet pawl 43 that has the generally V-shaped tapered bottom 43b (FIG. 8B) is fitted in the axial groove 62 of the feed screw shaft 49, as shown in FIG. 4B.
  • the motor M is driven by the drive switch 17, the rotational output shaft 27, and accordingly, the eccentric cone 47 are rotated through the reduction gear device 23, the spline 29 and the boss 31.
  • the ratchet lever 39 integral with the rotational drive shaft 27 is rotated for example in the counterclockwise direction in FIG.
  • the feed screw shaft 49 is rotated in the same direction by the one direction rotation transmission mechanism which is constituted by the ratchet pawl 43 and the axial groove 62.
  • the ratchet pawl 43 which is a driving element comes into contact at the left side face thereof with the left side wall of the axial groove 62, as shown in FIG. 5B.
  • the feed screw shaft (male thread) 49 which constitutes the feed screw mechanism together with the threaded hole (female thread) 51 of the nut member 53 with which the male thread engages axially moves in the right direction in FIG. 1.
  • the axial movement of the feed screw shaft 49 in the right direction is transmitted to the rotational drive shaft 27 and the eccentric cone 47 through the first spring 55.
  • the eccentric cone 47 axially moves while rotating to be strongly pressed against the front end of the pipe P to thereby spread (flare) the pipe end into a conical shape (FIGS. 5A and 5B).
  • the eccentric cone 47 Upon completion of the flaring, the eccentric cone 47 is no longer able to move in the axial direction, so that it idle-rotates in the flared pipe end while in contact therewith. Due to a further rotation of the motor M, the feed screw shaft 49 continues moving in the axial direction while compressing the first spring 55, so that the front portion of the ratchet pawl 43 of the ratchet lever 39 that has the first tapered bottom 43a (FIG. 8A) comes in the axial groove 62.
  • the ratchet pawl 43 (43a) idle-rotates while riding over the edge of the axial groove 62 for every one turn thereof, in view of the direction of the inclination of the ratchet pawl 43 (43a), as shown in FIGS. 6A and 6B.
  • the ratchet lever 39 idle-rotates, so that no rotation thereof can be transmitted to the feed screw shaft 49.
  • the operative connection between the rotational drive shaft 27 and the feed screw shaft 49 is broken, so that the operation of the one-direction rotation transmission mechanism becomes null.
  • the reason to idle the eccentric cone 47 after the flaring is completed is to prevent the tool (eccentric cone) from being damaged or destroyed due to an overload which would be otherwise produced and to obtain a uniform and precisely flared end face of the pipe P.
  • the ratchet lever 39 repeatedly swings about the pin 37 every time the ratchet pawl 43 (43a) rides over the edge of the axial groove 62.
  • the axial groove 62 of the feed screw shaft 49 constitutes a clutch which selectively releases the one-direction rotation transmission mechanism, that is, selectively disconnects the rotational drive shaft from the feed screw shaft, in accordance with the axial position of the feed screw shaft 49 (axial groove 62).
  • the flaring device Upon completion of the flaring, the motor M is reversed by the drive switch 17.
  • the flaring device basically operates in a way opposite to the above-mentioned operation at the forward rotation of the motor M, but in the reverse rotation, the ratchet pawl 43 comes into contact at the right end face thereof with the right wall surface of the axial groove 62, contrary to the operation at the forward rotation. Consequently, the rotation of the ratchet lever 39 (and accordingly, the rotational drive shaft 27) is transmitted to the feed screw shaft 49. Namely, upon reversing, the ratchet pawl 43 transmits the rotation to the feed screw shaft 49.
  • the ratchet pawl 43 (43c) idle-rotates while riding over the edge of the axial groove 62 for every turn, in view of the direction of the inclination of the bottom of the ratchet pawl 43, as shown in FIGS. 7A and 7B, similarly to FIGS. 6A and 6B.
  • the ratchet lever 39 idles, so that no rotation thereof can be transmitted to the feed screw shaft 49. That is, the functional connection of the rotational drive shaft 27 and the feed screw shaft 49 is broken. Thus, even if the motor M continues rotating, the rotational drive shaft idles to prevent the tool from being broken or damaged due to the overload.
  • the mechanism which idles the tool (eccentric cone) upon the completion of the flaring and the retraction of the eccentric cone can prevent the tool from being damaged or broken due to the overload.
  • a uniform flared surface of a good appearance can be obtained, regardless of the skill of the operator.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Plasma & Fusion (AREA)
  • Turning (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Transmission Devices (AREA)
  • Treatment Of Fiber Materials (AREA)
  • Press Drives And Press Lines (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
US07/665,461 1990-03-15 1991-03-06 Motor driven flaring device Expired - Fee Related US5090226A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2062714A JP2834264B2 (ja) 1990-03-15 1990-03-15 電動フレア工具
JP2-62714 1990-03-15

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US5090226A true US5090226A (en) 1992-02-25

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US (1) US5090226A (ja)
EP (1) EP0448304B1 (ja)
JP (1) JP2834264B2 (ja)
KR (1) KR930009928B1 (ja)
DE (1) DE69102175T2 (ja)
ES (1) ES2054440T3 (ja)
HK (1) HK1000659A1 (ja)

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US6708462B2 (en) 2001-03-07 2004-03-23 Johnson Controls Technology Company Foam-in-place seal and method
US20060117827A1 (en) * 2004-12-07 2006-06-08 Kao Meng J Tube expander
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US9962755B2 (en) 2013-10-30 2018-05-08 Ags Company Automotive Solutions, Llc Hand held flaring tool
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US20220176437A1 (en) * 2019-03-27 2022-06-09 Zhejiang Value Mechanical & Electrical Products Co., Ltd. Electric pipe expander, chuck structure for electric pipe expander, and control circuit for electric pipe expander
US11596999B2 (en) 2019-02-20 2023-03-07 Milwaukee Electric Tool Corporation PEX expansion tool
US11633775B2 (en) 2019-02-20 2023-04-25 Milwaukee Electric Tool Corporation PEX expansion tool
US11779990B2 (en) 2021-04-09 2023-10-10 Milwaukee Electric Tool Corporation Expansion tool
US11819902B2 (en) 2020-11-27 2023-11-21 Milwaukee Electric Tool Corporation Expansion tool

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JP2005324208A (ja) * 2004-05-12 2005-11-24 Matsushita Electric Works Ltd 電動フレア工具
TWM386419U (en) * 2010-02-11 2010-08-11 Lai Si Yu Automatic extruding device
DE102014102862A1 (de) * 2014-03-04 2015-09-10 Az Vermögensverwaltung Gmbh & Co. Kg Stauchvorrichtung für ein Wellrohr
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US6616393B1 (en) 2000-02-07 2003-09-09 Ball Corporation Link coupling apparatus and method for container bottom reformer
US6484550B2 (en) 2001-01-31 2002-11-26 Rexam Beverage Can Company Method and apparatus for necking the open end of a container
US6708462B2 (en) 2001-03-07 2004-03-23 Johnson Controls Technology Company Foam-in-place seal and method
US20060117827A1 (en) * 2004-12-07 2006-06-08 Kao Meng J Tube expander
US9492857B2 (en) 2010-08-06 2016-11-15 American Grease Stick Company Hand held flaring tool
US10850319B2 (en) 2010-08-06 2020-12-01 Ags Company Automotive Solutions, Llc Hand held flaring tool
CN103317039A (zh) * 2013-06-08 2013-09-25 宁波市生命力通讯科技有限公司 薄壁金属管气动扩孔器
CN103317039B (zh) * 2013-06-08 2015-05-13 宁波市生命力通讯科技有限公司 薄壁金属管气动扩孔器
US9962755B2 (en) 2013-10-30 2018-05-08 Ags Company Automotive Solutions, Llc Hand held flaring tool
US11072018B2 (en) 2013-10-30 2021-07-27 Ags Company Automotive Solutions Llc Hand held flaring tool
US20150321237A1 (en) * 2014-05-09 2015-11-12 Chen-Tzu Lin Structure of a tube expander
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CN107278175A (zh) * 2014-11-06 2017-10-20 安德尔技术波兰股份公司 改进的用于管端部扩口的扩口设备
CN107278175B (zh) * 2014-11-06 2019-05-10 安德尔技术波兰股份公司 改进的用于管端部扩口的扩口设备
US10702906B2 (en) * 2014-11-06 2020-07-07 Andel Technology Polska Sp. Z O.O. Flaring device for flaring the ends of pipes
US9975289B2 (en) 2016-07-27 2018-05-22 Black & Decker Inc. PEX expanding tool
CN107511431A (zh) * 2017-09-06 2017-12-26 国营芜湖机械厂 一种便携式飞机厚壁不锈钢导管旋压扩喇叭口成型工具
US11596999B2 (en) 2019-02-20 2023-03-07 Milwaukee Electric Tool Corporation PEX expansion tool
US11633775B2 (en) 2019-02-20 2023-04-25 Milwaukee Electric Tool Corporation PEX expansion tool
US20220176437A1 (en) * 2019-03-27 2022-06-09 Zhejiang Value Mechanical & Electrical Products Co., Ltd. Electric pipe expander, chuck structure for electric pipe expander, and control circuit for electric pipe expander
US20230294156A1 (en) * 2019-03-27 2023-09-21 Zhejiang Value Mechanical & Electrical Products Co., Ltd. Electric pipe expander
US11980924B2 (en) * 2019-03-27 2024-05-14 Zhejiang Value Mechanical & Electrical Products Co., Ltd. Electric pipe expander, chuck structure for electric pipe expander, and control circuit for electric pipe expander
CN112605200A (zh) * 2020-07-01 2021-04-06 真兰管业科技有限公司 一种管道翻边工装以及通过该工装使管件快速连接的方法
CN112605200B (zh) * 2020-07-01 2022-10-14 真兰管业科技有限公司 一种管道翻边工装以及通过该工装使管件快速连接的方法
US11819902B2 (en) 2020-11-27 2023-11-21 Milwaukee Electric Tool Corporation Expansion tool
US11779990B2 (en) 2021-04-09 2023-10-10 Milwaukee Electric Tool Corporation Expansion tool

Also Published As

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DE69102175T2 (de) 1994-10-27
KR910016425A (ko) 1991-11-05
EP0448304A3 (en) 1992-02-26
EP0448304B1 (en) 1994-06-01
EP0448304A2 (en) 1991-09-25
HK1000659A1 (en) 1998-04-17
JPH03268827A (ja) 1991-11-29
KR930009928B1 (ko) 1993-10-13
DE69102175D1 (de) 1994-07-07
ES2054440T3 (es) 1994-08-01
JP2834264B2 (ja) 1998-12-09

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